CN101865250B - Double clutch transmission - Google Patents

Double clutch transmission Download PDF

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Publication number
CN101865250B
CN101865250B CN201010163898.6A CN201010163898A CN101865250B CN 101865250 B CN101865250 B CN 101865250B CN 201010163898 A CN201010163898 A CN 201010163898A CN 101865250 B CN101865250 B CN 101865250B
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CN
China
Prior art keywords
gear
coupling
activated
clutch
plane
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Fee Related
Application number
CN201010163898.6A
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Chinese (zh)
Other versions
CN101865250A (en
Inventor
W·里格尔
M·赖施
J·瓦夫齐希
G·贡波尔茨贝格
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ZF Friedrichshafen AG
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ZF Friedrichshafen AG
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Publication date
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Publication of CN101865250A publication Critical patent/CN101865250A/en
Application granted granted Critical
Publication of CN101865250B publication Critical patent/CN101865250B/en
Expired - Fee Related legal-status Critical Current
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/006—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion power being selectively transmitted by either one of the parallel flow paths
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
    • F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
    • F16H2003/0807—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts with gear ratios in which the power is transferred by axially coupling idle gears
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
    • F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
    • F16H2003/0826—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts wherein at least one gear on the input shaft, or on a countershaft is used for two different forward gear ratios
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
    • F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
    • F16H3/087—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears
    • F16H3/093—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears with two or more countershafts
    • F16H2003/0931—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears with two or more countershafts each countershaft having an output gear meshing with a single common gear on the output shaft
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/0026—Transmissions for multiple ratios comprising at least one creep low gear, e.g. additional gear for extra low speed or creeping
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
    • F16H2200/006—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising eight forward speeds
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
    • F16H2200/0065—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising nine forward speeds
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/0082—Transmissions for multiple ratios characterised by the number of reverse speeds
    • F16H2200/0086—Transmissions for multiple ratios characterised by the number of reverse speeds the gear ratios comprising two reverse speeds
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/0082—Transmissions for multiple ratios characterised by the number of reverse speeds
    • F16H2200/0091—Transmissions for multiple ratios characterised by the number of reverse speeds the gear ratios comprising three reverse speeds
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/0082—Transmissions for multiple ratios characterised by the number of reverse speeds
    • F16H2200/0095—Transmissions for multiple ratios characterised by the number of reverse speeds the gear ratios comprising four reverse speeds
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/19—Gearing
    • Y10T74/19219—Interchangeably locked
    • Y10T74/19228—Multiple concentric clutch shafts

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Structure Of Transmissions (AREA)

Abstract

A double clutch transmission with two clutches with input sides connected to a drive shaft and output sides each respectively connected to one of two transmission input shafts disposed coaxially to one another. At least two countershafts are provided upon which toothed idler gearwheels are mounted in a rotatable manner and toothed fixed gearwheels are disposed on the two transmission input shafts in a rotationally fixed manner. At least one shift element is provided for connecting two idler gearwheels in a rotationally fixed manner such that at least several power shiftable forwards gears and/or at least one reverse gear can be shifted. A maximum of six gear planes are provided so that at least one power shiftable winding path gear can be shifted using the at least one shift element.

Description

Dual-clutch transmission
Technical field
The present invention relates to a kind of dual-clutch transmission.
background technique
Dual-clutch transmission by known six gears of file DE 10305241A1 or seven gears.This dual-clutch transmission comprises two clutches, and described clutch is connected with live axle with its input side respectively and is connected with in two transmission input shafts one respectively with its outlet side.Two transmission input shafts arrange coaxially with each other.In addition, two jack shafts are arranged to axis and are parallel to two transmission input shafts, the free gear of described two jack shafts and the engagement of the fixed gear of transmission input shaft.In addition, coupling axially movably rotationally fixedly is fixed on jack shaft, to can connect corresponding shift gear.The velocity ratio of corresponding selection is delivered on differential mechanism by output gear.In order to realize the gear stage of expectation in known dual-clutch transmission, need a plurality of gear planes, making must not be inapparent structure space when mounted.
In addition, by the wheeled speed changer of the known Cylinder Gear of file DE3822330A1.The wheeled speed changer of this Cylinder Gear comprises the double clutch that can shift gears under load, and its part is connected with live axle and its another part is connected with the driving hollow shaft can be rotated to support on live axle.For definite velocity ratio, live axle can be coupled with driving hollow shaft by switching member.
By the known power-shift transmission with two clutches of file DE102004001961A1, described clutch is equipped on respectively a minute speed changer.The transmission input shaft of two minutes speed changers arranges coaxially with each other and meshes by fixed gear and the free gear of the jack shaft setting.The corresponding free gear of jack shaft can be connected with corresponding jack shaft by means of the switching member rotationally fixedly setting.By known a kind of eight shift transmissions of this document, another switching member is wherein set for being coupled two transmission input shafts to realize another gear stage.In this structure, seven shift transmissions just needed at least six gear planes in speed changer at two minutes, to can realize each gear stage.This causes structure length undesirable prolongation vertically, has made significant limitation and has been installed to the installation possibility in car.
In addition by the known another kind of power-shift transmission of file DE102005028532A1, it comprises two input shafts and a jack shaft only.For example eight shift transmissions need at least seven gear planes in this structure, to can realize each gear stage.This causes structure length less desirable prolongation vertically.
summary of the invention
Therefore the object of the invention is, advise a kind of dual-clutch transmission that starts described type, in this dual-clutch transmission, with the least possible member, realize the gear stage that a plurality of motilities are shifted gears as far as possible economically and when structure space demand is little.
This object realizes by having the dual-clutch transmission of following characteristics according to the present invention, that is: dual-clutch transmission has: two clutches, and the input side of described clutch is connected with a live axle and the outlet side of described clutch is connected with in the transmission input shaft of two mutual coaxial settings one respectively, at least two jack shafts, the rotatably mounted shift gear that is configured to free gear on described two jack shafts, rotationally fixedly is arranged on shift gear on two transmission input shafts and that be configured to fixed gear, and described fixed gear is meshed with free gear at least in part, a plurality of couplings, for making free gear rotationally fixedly be connected with jack shaft, be arranged on each output gear on two jack shafts, described output gear is coupled mutually with the tooth portion of a driven shaft respectively, and at least one switching member, be used for making two shift gear rotationally fixedlies to connect, wherein at least can connect a plurality of forward gear and at least one reverse gear shift that can power gear shifting, it is characterized in that, be provided with maximum six gear planes, wherein be provided with at least one Double-gear plane, and each free gear of the first and second jack shafts is equipped on a fixed gear of one of transmission input shaft in each Double-gear plane, wherein in each Double-gear plane, at least one free gear can be used at least two gears, thereby can connect by least one switching member the roundabout gear that at least one can power gear shifting.
Thus, advise the dual-clutch transmission that a kind of structure space is optimized, have two clutches, its input side is connected with live axle, and its outlet side respectively with for example two coaxially to each other in the transmission input shafts of setting be connected.Described dual-clutch transmission comprises at least two jack shafts or like, the shift gear that is configured to free gear can be rotated to support on described jack shaft, is wherein provided with shift gear rotationally fixedly setting and that be configured to fixed gear on two transmission input shafts, that be meshed with free gear at least in part.In addition, be provided with a plurality of couplings for free gear is connected with jack shaft rotationally fixedly.Dual-clutch transmission according to the present invention has: be arranged on each output gear or constant small gear (Konstantenritzel) on each jack shaft, described output gear or constant small gear are coupled with a tooth portion of live axle respectively, to corresponding jack shaft is connected with output unit; And at least one can activate or switching member that can be closed or like as so-called roundabout gear-switching member, for rotationally fixedly, connect two shift gears, wherein can realize a plurality of gears that can power gear shifting.
According to the present invention, the dual-clutch transmission of advising preferably includes maximum six gear planes, realizes the gear of at least seven motility gearshifts by these gear planes with less structure space demand.For example described maximum six gear planes can form by least one Double-gear plane, wherein, in each Double-gear plane, a free gear of the first and second jack shafts is equipped on respectively a fixed gear of one of transmission input shaft, and at least one free gear can be used at least two gears, make it possible to connect at least two roundabout gears (Windungsgang) by least one switching member.
Except Double-gear plane, also can use individual gears plane, wherein the free gear of a jack shaft is equipped on to a fixed gear of one of transmission input shaft in each individual gears plane.Other layout (konstellation) is also possible.
Due to the possible repeatedly utilization of free gear, in advised dual-clutch transmission, can utilize the least possible gear plane can realize maximum velocity ratio quantity, wherein preferably the first seven forward gear is motility gearshift when order is carried out.
In order to optimize speed ratio interval in the dual-clutch transmission in the suggestion according to the present invention, by replacing a fixed gear with two fixed gears, also can replace a for example Double-gear plane by two individual gears planes.Can realize thus gear speed ratio special coordination, progressive interval.Also can replace two individual gears planes by a Double-gear plane.
The dual-clutch transmission of advising can be preferably configured as 8 shift transmissions of the gear level with at least seven motility gearshifts.Owing to comparing with known gearbox arrangement, short structural type dual-clutch transmission according to the present invention is specially adapted to the front cross mounting type in vehicle.But also can adopt according to the type of considered vehicle and structure space situation other mounting type.
In advised dual-clutch transmission, the first and the 8th forward gear can be preferably roundabout gear.In addition, reverse gear shift and/or each other gear, can be configured to equally roundabout gear and may also can be configured to motility gearshift as creeper gear or overgear.
In advised dual-clutch transmission, advantageously obtain one can power gear shifting to the seven forward gears additional overgear as the 8th forward gear of optional motility gearshift, thus can fuel saving in this vehicle.
For example can set for example four free gears that can switch to the first jack shaft according to the difference of structure, and set for example three or four free gears that can switch to the second jack shaft, described in each, free gear meshes with the fixed gear of the transmission input shaft setting respectively.
If last or penultimate speed ratio interval (Gangsprung) are designed to higher than the speed ratio interval being correspondingly positioned at before it, in the downshift by driver requested, can provide extra high output torque or driving power.
In dual-clutch transmission according to the present invention, advantageously on a jack shaft, need maximum five switching positions.On two jack shafts, altogether adopt generally only nine switching positions, to realize the gear level of advising.
According to the present invention, can set, by at least one the additional switching member on the first jack shaft, can make the free gear of second minute speed changer be connected with the free gear of first minute speed changer, by switching member, at least can correspondingly as roundabout gear, connect first forward gear and/or the 8th forward gear and/or at least one creeper gear and/or at least one overgear thus.
In addition can set, by the optional or additional switching member on the second jack shaft, can make the free gear of second minute speed changer be connected with the free gear of first minute speed changer, wherein by switching member, can correspondingly as roundabout gear, connect the first forward gear and/or the 8th forward gear and/or reverse gear shift and/or creeper gear and/or overgear.
Therefore utilize according to dual-clutch transmission of the present invention can be at least by least one switching member or also can realize roundabout gear by two switching members, shift gear at two minutes speed changers of described each roundabout gear is coupled mutually, to realize by the kinetic current of two minutes speed changers thus.Here the switching member correspondingly adopting is used for making two free gears to be coupled and to make thus two transmission input shafts interrelated.
In dual-clutch transmission, for the layout of the switching member that two definite free gears are coupled can be changed, so switching member is not necessarily must be arranged between the free gear that will be coupled.Therefore also it is contemplated that other position of corresponding switching member, to for example optimize the connection on actuating device.
In dual-clutch transmission, according to a kind of possible structure, can set, two fixed gears on the second transmission input shaft that is included in second minute speed changer as the first gear plane and the second gear plane of Double-gear plane respectively, are wherein included in two fixed gears on the first transmission input shaft of first minute speed changer as the 4th and the 5th gear plane of Double-gear plane respectively.
In the scope of another embodiment of the present invention, also can set, in advised dual-clutch transmission as the first gear plane of individual gears plane be included in two fixed gears on the second transmission input shaft of second minute speed changer as the second gear plane of Double-gear plane, wherein respectively as the 3rd gear plane and the 4th gear plane of individual gears plane with can comprise three fixed gears of the first transmission input shaft of first minute speed changer as the 5th gear plane of Double-gear plane.Also can make the 5th gear plane be configured to individual gears plane, and a 6th additional gear plane is set as individual gears plane, it is equipped on another fixed gear of the first transmission input shaft.
In next embodiment of this external dual-clutch transmission, can set, as three fixed gears of the first gear plane of Double-gear plane and the second transmission input shaft of comprising second minute speed changer as the second gear plane and the 3rd gear plane of individual gears plane respectively, two fixed gears on the first transmission input shaft that wherein comprises first minute speed changer as the 4th gear plane and the 5th gear plane of Double-gear plane respectively.Also the 5th gear plane can be configured to individual gears plane, and a 6th additional gear plane be set as individual gears plane, it is equipped on another fixed gear on the first transmission input shaft of first minute speed changer.
In order to set in dual-clutch transmission according to the present invention for realizing the essential rotating speed reversing of reverse gear shift, such as using at least one such as the intermediate gear or the like that are arranged on countershaft etc.Also can be by the intermediate gear that acts at least one reverse gear shift for one of free gear of a jack shaft.For reverse gear shift velocity ratio, do not need additional countershaft like this, because one of described free gear not only meshes with a fixed gear but also with another switchable free gear of another jack shaft.For the essential intermediate gear of reverse gear shift, as switchable free gear, be arranged on a jack shaft and for realizing at least another forward gear thus.This intermediate gear also can be configured to cone pulley (Stufenrad), and is arranged on jack shaft and is also arranged on additional countershaft and has nothing to do with this gear.Also can not be that intermediate gear is arranged on to one of existing jack shaft is upper, but be for example arranged on another axle separating, for example, on the 3rd jack shaft.
In order to obtain desired gear stage, in dual-clutch transmission according to the present invention, can set, at least one beidirectional coupling or like are set on each jack shaft.The coupling setting can correspondingly make a free gear rotationally fixedly setting be connected with jack shaft according to the difference of steering activating under closed in other words state.Coupling or the like of single effect are set at least one that in addition also can be in jack shaft.For example can use blade tooth clutch that hydraulic pressure, electricity, pneumatic, mechanically operated clutch or shape are sealed and any type of synchronizer as coupling, they are for making a free gear be connected with a jack shaft rotationally fixedly.A beidirectional coupling also can replace by the coupling of two single effects, and vice versa.
Also it is contemplated that, change the illustrated layout possibility of shift gear and also can change the quantity of shift gear and the quantity of coupling, to realize other motility gearshift or gear, structure space that can not power gear shifting be saved and member is saved in advised dual-clutch transmission.Especially each fixed gear of Double-gear plane can be divided into two fixed gears for two individual gears planes.Can improve speed ratio interval thus.Can exchange in addition (exchange) jack shaft.Also can exchange a minute speed changer, that is, around vertical axis, form mirror image.Now exchange hollow shaft and solid shaft.For example minimum gear can be arranged on solid shaft thus, to further optimize the utilization in existing structure space.In addition can exchange adjacent gear plane, for example, to optimize bending shaft and/or connect best gearshift actuating device.In addition can change the corresponding position of coupling in gear plane.In addition also can change the action direction of coupling.
Here the gear numbering adopting freely defines.Also can add creeper gear and/or overgear, to for example improve cross-country characteristic or accelerating performance in vehicle.In addition for example can save the first gear, for example, to can optimize better the integrity at speed ratio interval.In these measures, reasonably change gear numbering.
Irrelevant with the corresponding embodiment of dual-clutch transmission, live axle and driven shaft can not be preferably mutually to arrange coaxially yet, and this has realized a kind of layout of special saving structure space.For example make the axle that spatially front and back set gradually thus also can slightly stagger each other.In this layout, can mesh to realize the direct gear that is 1 with velocity ratio and can advantageously relatively freely be placed into the 6th to the 9th by tooth and block.Also it is contemplated that other layout possibility of live axle and driven shaft.
The dual-clutch transmission of advising is preferably equipped with integrated output stage.This output stage can comprise that a fixed gear on driven shaft is as output gear, this fixed gear not only meshes with first output gear as fixed gear of the first jack shaft, and meshes with second output gear as fixed gear of the second jack shaft.But also at least one in each output gear can be configured to the gear that can switch.For example a coupling can be equipped on at least one output gear, this coupling is removed being connected between the jack shaft that sets and output gear under open mode for this reason.
Can advantageously by a startup clutch or shift clutch, operate low forward gear and reverse gear shift, to thus higher load is focused on this clutch, and can on structure space and cost, more advantageously form second clutch thus.In advised dual-clutch transmission, particularly gear plane can be set like this, make not only can by inner transmission input shaft or also can by outside transmission input shaft and thus can by correspondingly better applicable clutch start, this also can realize in the structural type concentric setting, radially mutually nested of double clutch.Can make for this reason gear plane correspondingly mirror image arrange symmetrically or exchange.
Have nothing to do with corresponding embodiment's scheme, in dual-clutch transmission, for example also can exchange the gear plane of setting.
Accompanying drawing explanation
By means of accompanying drawing, describe the present invention in detail below.Wherein:
Fig. 1 illustrates according to the schematic diagram of the first embodiment of eight gear dual-clutch transmissions of the present invention;
Fig. 2 illustrates by the gearshift figure of the first embodiment of Fig. 1;
Fig. 3 illustrates according to the schematic diagram of the second embodiment of eight gear dual-clutch transmissions of the present invention;
Fig. 4 illustrates by the gearshift figure of the second embodiment of Fig. 3;
Fig. 5 illustrates according to the schematic diagram of the 3rd embodiment of eight gear dual-clutch transmissions of the present invention;
Fig. 6 illustrates by the gearshift figure of the 3rd embodiment of Fig. 5;
Fig. 7 illustrates according to the schematic diagram of the 4th embodiment of eight gear dual-clutch transmissions of the present invention;
Fig. 8 illustrates by the gearshift figure of the 4th embodiment of Fig. 7;
Fig. 9 illustrates according to the schematic diagram of the 5th embodiment of eight gear dual-clutch transmissions of the present invention; And
Figure 10 illustrates by the gearshift figure of the 5th embodiment of Fig. 9.
Embodiment
A possible embodiment of eight gear dual-clutch transmissions is shown respectively in Fig. 1,3,5,7 and 9.In Fig. 2,4,6 and 8, figure out the corresponding gearshift figure for different embodiments.
Described eight gear dual-clutch transmissions comprise two clutch K1, K2, the input side of described clutch is connected with live axle w_an, and its output end is connected with a transmission input shaft in two transmission input shaft w_k1, w_k2 that arrange coaxially to each other respectively.In addition torshional vibration damper 19 can be set on live axle w_an.Be provided with in addition two jack shaft w_v1, w_v2, the rotatably mounted shift gear that is configured to free gear 8,9,10,11,12,13,14,15 on described jack shaft.On two transmission input shaft w_k1, w_k2, rotationally fixedly setting is configured to the shift gear of fixed gear 1,2,3,4,5,6, and described shift gear meshes with free gear 8,9,10,11,12,13,14,15 at least in part.
For free gear 8,9,10,11,12,13,14,15 can be connected with corresponding jack shaft w_v1, w_v2, on jack shaft w_v1, w_v2, be provided with a plurality of coupling A, B, C, D, E, F, G, H that can be activated.External two jack shaft w_v1, w_v2 are upper as constant small gear, output gear 17,18 is set for this, described output gear is coupled with the tooth portion of a fixed gear 16 of a driven shaft w_ab respectively, and wherein corresponding output stage i_ab_1, i_ab_2 are equipped on output gear 17,18.
Except realizing the anti-described coupling A being rotatably connected between shift gear and the jack shaft w_v1, the w_v2 that set, B, C, D, E, F, G, H, at described dual-clutch transmission, be also provided with at least one roundabout gear-switching member I, K, for rotationally fixedly, connect two shift gears of jack shaft w_v1, a w_v2, thereby realize at least one roundabout gear.
According to the present invention, in dual-clutch transmission, be provided with maximum six gear plane 8-1,8-12,9-2,9-13,3-13,10-3,4-14,10-14,11-5,11-15,6-15, wherein in each embodiment, be provided with at least one Double-gear plane 8-12,9-13,10-14,11-15, make the switching member I, the K that by least one, are activated can connect at least two roundabout gears.As switching member I, K, can adopt respectively for example pawl or like, for two gears or like are connected.
If there is switching member K, it is upper that this switching member K is arranged on the second jack shaft w_v2, makes free gear 13 be connected with free gear 14 while being activated with convenient switching member K.If there is switching member I, it is upper that this switching member I is arranged on the first jack shaft w_v1, makes free gear 9 be connected with free gear 10 while being activated with convenient switching member I.
In pressing the first embodiment of Fig. 1, in the first gear plane 8-12 as Double-gear plane, the fixed gear 1 of the second transmission input shaft w_k2 both meshes with the free gear 12 of the second jack shaft w_v2, also meshes with the free gear 8 of the first jack shaft w_v1.Unlike this, in pressing the 4th embodiment of Fig. 7, fixed gear 1 is not directly, but indirectly by the intermediate gear ZR on a countershaft w_zw and free gear 8 engagements, wherein, described intermediate gear ZR now meshes with the free gear 8 of the first jack shaft w_v1.By means of intermediate gear ZR, realized for realizing the rotating speed reversion of each reverse gear shift velocity ratio.In the first and the 4th embodiment, in the second gear plane 9-2 as individual gears plane, the fixed gear 2 of the second transmission input shaft w_k2 and 9 engagements of the free gear of the first jack shaft w_v1, and in the 3rd gear plane 3-13 as individual gears plane, the fixed gear 3 of the second transmission input shaft w_k2 and 13 engagements of the free gear of the second jack shaft w_v2.
According to the first embodiment, in the 4th gear plane 10-14 as Double-gear plane, the fixed gear 4 of the first transmission input shaft w_k1 both meshed with the free gear 10 of the first jack shaft w_v1, also with countershaft w_zw for rotating speed reversion on intermediate gear ZR engagement, wherein intermediate gear ZR in addition with free gear 14 engagements of the second jack shaft w_v2.In addition, in the 5th gear plane 11-5 as individual gears plane, the fixed gear 5 of the first transmission input shaft w_k1 and 11 engagements of the free gear of the first jack shaft w_v1.In the 6th gear plane 6-15 as individual gears plane, the fixed gear 6 of the first transmission input shaft w_k1 and 15 engagements of the free gear of the second jack shaft w_v2.
Unlike this, in the 4th embodiment, in the 4th gear plane 10-14 as Double-gear plane, the fixed gear 4 of the first transmission input shaft w_k1 both meshes with the free gear 10 of the first jack shaft w_v1, also meshes with the free gear 14 of the second jack shaft w_v2.In the 5th gear plane 11-15 as Double-gear plane, the fixed gear 5 of the first transmission input shaft w_k1 both meshes with the free gear 11 of the first jack shaft w_v1, also meshes with the free gear 15 of the second jack shaft w_v2.
In pressing the second embodiment of Fig. 3, in the first gear plane 8-12 as Double-gear plane, the fixed gear 1 of the second transmission input shaft w_k2 both meshes with the free gear 8 of the second jack shaft w_v2, also meshes with the free gear 12 of the second jack shaft w_v2.In the second gear plane 9-13 as Double-gear plane, the fixed gear 2 of the second transmission input shaft w_k2 both meshes with the free gear 9 of the first jack shaft w_v1, also meshes with the free gear 13 of the second jack shaft w_v2.In addition, in the 3rd gear plane 10-14 as Double-gear plane, the fixed gear 3 of the first input shaft w_k1 both meshed with the free gear 10 of the first jack shaft w_v1, also mesh with the free gear 14 of the second jack shaft w_v2, and in the 4th gear plane 11-15 as Double-gear plane, the fixed gear 4 of the first transmission input shaft w_k1 both with the free gear 11 of the first jack shaft w_v1 also with countershaft w_zw for rotating speed reversion on intermediate gear ZR engagement, wherein, this intermediate gear ZR also meshes with the free gear 15 of the second jack shaft w_v2 in addition.
According to the 3rd and the 5th embodiment of pressing Fig. 5 and 6, in the first gear plane 8-1 as individual gears plane, the fixed gear 1 of the second transmission input shaft w_k2 and 8 engagements of the free gear of the first jack shaft w_v1.In the second gear plane 9-13 as Double-gear plane, the fixed gear 2 of the second transmission input shaft w_k2 both meshes with the free gear 9 of the first jack shaft w_v1, also meshes with the free gear 13 of the second jack shaft w_v2.In the 3rd gear plane 10-3 as individual gears plane, the fixed gear 3 of the first transmission input shaft w_k1 and 10 engagements of the free gear of the first jack shaft w_v1, and in the 4th gear plane 4-14 as individual gears plane, the fixed gear 1,4 of the first transmission input shaft w_k1 and 14 engagements of the free gear of the second jack shaft w_v2.Finally, in the 3rd embodiment, in the 5th gear plane 11-15 as Double-gear plane, the fixed gear 5 of the first transmission input shaft w_k1 both meshed with the free gear 11 of the first jack shaft w_v1, also with countershaft w_zw for rotating speed reversion on intermediate gear ZR engagement, wherein this intermediate gear ZR again with free gear 15 engagements of the second jack shaft w_v2.Unlike this, in the 5th embodiment, in the 5th gear plane 11-5 as individual gears plane, the fixed gear 5 of the first transmission input shaft w_k1 and 11 engagements of the free gear of the first jack shaft w_v1, and in the 6th gear plane 6-15 as individual gears plane, the fixing tooth 6 of the first transmission input shaft w_k1 meshes with the intermediate gear ZR on the countershaft w_zw of rotating speed reversion, and wherein this intermediate gear ZR meshes with the free gear 15 of the second jack shaft w_v2 again.
In all embodiments, on the first jack shaft w_v1, between the first gear plane 8-12 or 8-1 and the second gear plane 9-2 or 9-13, be provided with beidirectional coupling A-B, the coupling A being wherein activated is permanently connected free gear 8 and the first jack shaft w_v1, and the coupling B being activated is permanently connected free gear 9 and the first jack shaft w_v1.This external first jack shaft w_v1 is upper arranges beidirectional coupling C-D between the 3rd gear plane 10-14,10-3 or the 4th gear plane 10-14 and the 4th gear plane 11-15 or the 5th gear plane 11-5,11-15, the coupling C being wherein activated is permanently connected free gear 10 and the first jack shaft w_v1, and the coupling D being activated is permanently connected free gear 11 and the first jack shaft w_v1.
In pressing Fig. 1,3,5 and 9 the first, second, third and the 5th embodiment, on the second jack shaft w_v2, at the 3rd gear plane 10-14 or the 4th gear plane 10-14, between 4-14 and the 4th gear plane 11-15 or the 5th gear plane 11-15 or the 6th gear plane 6-15, be provided with beidirectional coupling G-H, the coupling G being wherein activated is permanently connected free gear 14 and the second jack shaft w_v2, and the coupling H being activated is permanently connected free gear 15 and the second jack shaft w_v2.
In addition, in pressing Fig. 1,3 and 7 first, second and the 4th embodiment, between the first gear plane 8-12 and the second gear plane 9-13 or the 3rd gear plane 3-13, beidirectional coupling E-F is set, the coupling E being wherein activated is permanently connected free gear 12 and the second jack shaft w_v2, and the coupling F being activated is permanently connected free gear 13 and the second jack shaft w_v2.
In pressing the 3rd and the 5th embodiment of Fig. 5 and 9, on the second jack shaft w_v2, a single effect coupling F is equipped on to the second gear plane 9-13, the coupling F being wherein activated is permanently connected free gear 13 and the second jack shaft w_v2.
Finally, in pressing the 4th embodiment of Fig. 7, on the second jack shaft w_v2, the coupling H that sets a single effect to the 5th gear plane 11-15, the coupling H being wherein activated is permanently connected free gear 15 and the upper free gear 15 of the second jack shaft w_v2.
In dual-clutch transmission according to the present invention, be provided with an integrated output stage, this output stage has with the anti-output gear being rotatably connected 17 of the first jack shaft w_v1 and is arranged on the output gear 18 on the second jack shaft w_v2.Output gear 17 and output gear 18 mesh with a fixed gear 16 of driven shaft w_ab respectively.But output gear 17 or 18 with the jack shaft w_v1 setting or w_v2 between can realize by switchable coupling S_ab1 or S_ab2 switchable connection also.For example coupling S_ab1 can be equipped on to output gear 17, and coupling S_ab2 is equipped on to output gear 18.
With corresponding embodiment independently, in dual-clutch transmission according to the present invention, obtain, at least forward gear G1 to G8 is configured to motility gearshift.According to the difference of embodiment, additionally also reverse gear shift and/or creeper gear and/or overgear for example can be configured to motility gearshift to roundabout gear.For each embodiment, by the gearshift figure the following describes, draw details.
By the sample chart shown in Fig. 2 illustrate by the first embodiment's the gearshifts of the eight gear dual-clutch transmissions of Fig. 1 and scheme.
By this gearshift, figure draws, the first forward gear G1 can be by first clutch K1 and the coupling being activated F and the switching member I being activated as connect/break-make of roundabout gear (schaltbar), the second forward gear G2 can connect by second clutch K2 and the coupling being activated F, the 3rd forward gear G3 can connect by first clutch K1 and the coupling being activated C, the 4th forward gear G4 can connect by second clutch K2 and the coupling being activated B, the 5th forward gear G5 can connect by first clutch K1 and the coupling being activated D, the 6th forward gear G6 can connect by second clutch K2 and the coupling being activated E, the 7th forward gear G7 can connect by first clutch K1 and the coupling being activated H, the 8th forward gear G8 can connect as roundabout gear by second clutch K1 and the coupling being activated A and the switching member I being activated.
In addition, in the first embodiment, chart as shown in Figure 2 draws, a reverse gear shift R1 can connect by first clutch K1 and the coupling being activated G.Next reverse gear shift R2 can and connect as roundabout gear by second clutch K2, the coupling B being activated, the coupling D being activated and the coupling G being activated when coupling S_ab1 opens.In addition, for example another reverse gear shift R3 can and connect as roundabout gear by first clutch K1, the coupling B being activated, the coupling E being activated and the coupling G being activated when coupling S_ab2 opens.
In addition, in advised dual-clutch transmission, by the first embodiment, a creeper gear C1 can and connect as roundabout gear by second clutch K2, the coupling C being activated, the coupling F being activated and the coupling H being activated when coupling S_ab2 opens.In addition, a creeper gear C2 can and connect as roundabout gear by second clutch K2, the coupling D being activated, the coupling F being activated and the coupling H being activated when coupling S_ab1 opens.
In addition, in the first embodiment, overgear O1 can connect as roundabout gear by second clutch K2 and the coupling being activated H and the switching member I being activated.In addition, an overgear O2 can and connect as roundabout gear by second clutch K2, the coupling B being activated, the coupling F being activated and the coupling H being activated when coupling S_ab2 opens.
By the sample chart shown in Fig. 4 illustrate by the second embodiment's the gearshifts of the eight gear dual-clutch transmissions of Fig. 3 and scheme.
By this gearshift, figure draws, the first forward gear G1 can connect as roundabout gear by first clutch K1 and the coupling being activated E and the switching member K being activated, the second forward gear G2 can connect by second clutch K2 and the coupling being activated E, the 3rd forward gear G3 can connect by first clutch K1 and the coupling being activated G, the 4th forward gear G4 can connect by second clutch K2 and the coupling being activated F, the 5th forward gear G5 can connect by first clutch K1 and the coupling being activated D, the 6th forward gear G6 can connect by second clutch K2 and the coupling being activated A, the 7th forward gear G7 can connect by first clutch K1 and the coupling being activated C, the 8th forward gear G8 can connect as roundabout gear by first clutch K1 and the coupling being activated B and the switching member K being activated.
In addition,, in the second embodiment, by drawing at the chart shown in Fig. 4, a reverse gear shift R1 can connect by first clutch K1 and the coupling being activated H.In addition, another reverse gear shift R2 for example can and connect as roundabout gear by second clutch K2, the coupling A being activated, the coupling C being activated and the coupling H being activated when coupling S_ab1 opens.
In addition, overgear O1 can connect as roundabout gear by second clutch K2 and the coupling being activated C and the switching member K being activated.
By the sample chart shown in Fig. 6 illustrate by the 3rd embodiment's for eight gear dual-clutch transmissions of Fig. 5 gearshift and scheme.
By gearshift, figure draws, the first forward gear G1 can and connect as roundabout gear by the switching member I activating by first clutch K1 and the coupling being activated F, the second forward gear G2 can connect by second clutch K2 and the coupling being activated F, the 3rd forward gear G3 can connect by first clutch K1 and the coupling being activated C, the 4th forward gear G4 can connect by second clutch K2 and the coupling being activated B, the 5th forward gear G5 can connect by first clutch K1 and the coupling being activated G, the 6th forward gear G6 can connect by second clutch K2 and the coupling being activated A, the 7th forward gear G7 can connect by first clutch K1 and the coupling being activated D, the 8th forward gear G8 can and connect as roundabout gear by the switching member K being activated by first clutch K1 and the coupling being activated B.
In the 3rd embodiment, by also drawing at the chart shown in Fig. 6, a reverse gear shift R1 can and connect as roundabout gear by second clutch K2, the coupling C being activated, the coupling E being activated and the coupling G being activated when coupling S_ab2 opens.In addition, a reverse gear shift R2 can connect as roundabout gear by first clutch K1, the coupling A being activated, the coupling C being activated and the coupling E being activated when coupling S_ab1 opens.Next reverse gear shift R3 can connect as roundabout gear by second clutch K2 and the switching member being activated H and the switching member K being activated.In addition, a reverse gear shift R4 can and connect as roundabout gear by second clutch K2, the coupling B being activated, the coupling D being activated and the coupling H being activated when coupling S_ab1 opens.Finally, another reverse gear shift R5 can and connect as roundabout gear by second clutch K2, the coupling C being activated, the coupling F being activated and the coupling H being activated when coupling S_ab2 opens.
In addition, creeper gear C1 can connect as roundabout gear by second clutch K2 and the coupling being activated C and the switching member K being activated.In addition, a creeper gear C2 can and connect as roundabout gear by first clutch K1, the coupling A being activated, the coupling C being activated and the coupling F being activated when coupling S_ab1 opens.
In addition, overgear O1 can connect as roundabout gear by second clutch K2 and the coupling being activated D and the switching member I being activated.In addition, an overgear O2 can and connect as roundabout gear by second clutch K2, the coupling A being activated, the coupling C being activated and the coupling G being activated when coupling S_ab1 opens.Finally, overgear O3 also can connect as roundabout gear by first clutch K1 and the coupling being activated A and the switching member K being activated.
By the sample chart shown in Fig. 8 illustrate by the 4th embodiment's for eight gear dual-clutch transmissions of Fig. 7 gearshift and scheme.
By gearshift, figure draws, the first forward gear G1 can connect as roundabout gear by first clutch K1 and the coupling being activated E and the switching member I being activated, the second forward gear G2 can connect by second clutch K2 and the coupling being activated E, the 3rd forward gear G3 can connect by first clutch K1 and the coupling being activated C, the 4th forward gear G4 can connect by second clutch K2 and the coupling being activated B, the 5th forward gear G5 can connect by first clutch K1 and the coupling being activated H, the 6th forward gear G6 can connect by second clutch K2 and the coupling being activated F, the 7th forward gear G7 can connect by first clutch K1 and the coupling being activated D, the 8th forward gear G8 can connect as roundabout gear by second clutch K2 and the coupling being activated C and the switching member K being activated.
In the 4th embodiment, by also drawing in the chart shown in Fig. 8, a reverse gear shift R1 can and connect as roundabout gear by the switching member K activating by first clutch K1 and the coupling being activated A as roundabout gear connection and/or another reverse gear shift R2 by second clutch K2, the coupling A being activated, the coupling D being activated and the coupling G being activated and when coupling S_ab1 opens.In addition, another reverse gear shift R3 can and connect as roundabout gear by first clutch K1, the coupling A being activated, the coupling C being activated and the coupling E being activated when coupling S_ab1 opens.
In addition, in advised dual-clutch transmission, according to the 4th embodiment, creeper gear C1 can by second clutch K2, the coupling C being activated, the coupling E being activated, the coupling H being activated and when coupling S_ab2 opens as roundabout gear break-make.
In addition, overgear O1 can connect as roundabout gear by second clutch K2 and the coupling being activated D and the switching member I being activated.Another overgear O2 can and connect as roundabout gear by second clutch K2, the coupling D being activated, the coupling F being activated and the coupling H being activated when coupling S_ab2 opens.Finally, an overgear O3 can and connect as roundabout gear by first clutch K1, the coupling B being activated, the coupling D being activated and the coupling F being activated when coupling S_ab1 opens.
By the sample chart shown in Figure 10 illustrate by the gearshift of the 5th embodiment for eight gear dual-clutch transmissions of Fig. 9 and scheme.
By gearshift, figure draws, the first forward gear G1 can connect as roundabout gear by first clutch K1 and the coupling being activated B and the switching member K being activated, the second forward gear G2 can connect by second clutch K2 and the coupling being activated B, the 3rd forward gear G3 can connect by first clutch K1 and the coupling being activated G, the 4th forward gear G4 can connect by second clutch K2 and the coupling being activated F, the 5th forward gear G5 can connect by first clutch K1 and the coupling being activated C, the 6th forward gear G6 can connect by second clutch K2 and the coupling being activated A, the 7th forward gear G7 can connect by first clutch K1 and the coupling being activated D, the 8th forward gear G8 can connect as roundabout gear by first clutch K1 and the coupling being activated F and the switching member I being activated.
In the 5th embodiment, by also drawing in the chart shown in Figure 10, a reverse gear shift R1 can and connect as roundabout gear by first clutch K1, the coupling A being activated, the coupling E being activated and the coupling G being activated when coupling S_ab2 opens.In addition, another reverse gear shift R2 can and connect as roundabout gear by first clutch K1, the coupling B being activated, the coupling E being activated and the coupling G being activated when coupling S_ab2 opens.In addition, a reverse gear shift R3 can and connect as roundabout gear by second clutch K2, the coupling C being activated, the coupling F being activated and the coupling H being activated when coupling S_ab2 opens.In addition, a reverse gear shift R4 can and connect as roundabout gear by second clutch K2, the coupling D being activated, the coupling F being activated and the coupling H being activated when coupling S_ab2 opens.In addition, a reverse gear shift R5 can connect by first clutch K1 and the coupling being activated H.
In addition, creeper gear C1 can connect as roundabout gear by second clutch K2 and the coupling being activated G and the COMM communication I being activated.In addition, another creeper gear C2 can and connect as roundabout gear by second clutch K2, the coupling B being activated, the coupling D being activated and the coupling G being activated when coupling S_ab1 opens.
In addition, overgear O1 can connect as roundabout gear by second clutch K2 and the coupling being activated D and the switching member K being activated.Overgear O2 can connect as roundabout gear by first clutch K1 and the coupling being activated A and the switching member I being activated.Finally, an overgear O3 can and connect as roundabout gear by first clutch K1, the coupling B being activated, the coupling D being activated and the coupling F being activated when coupling S_ab1 opens.
By the gearshift figure according to Fig. 2, drawn particularly, in the first forward gear G1, from first clutch K1, use gear stage i_3, i_4 and i_2, wherein in order to be coupled two minutes speed changers, activate switching member I.In the second forward gear G2, use gear stage i_2, in the 3rd forward gear G3, use gear stage i_3, in the 4th forward gear G4, use gear stage i_4, in the 5th forward gear G5, use gear stage i_5, in the 6th forward gear G6, use gear stage i_6, and use gear stage i_7 in the 7th forward gear G7.In the 8th forward gear G8, from first clutch K1, use gear stage or gear level i_3, i_4 and ZW_8, wherein two minutes speed changers are coupled by switching member I in the first embodiment.
In addition, in reverse gear shift R1, use gear stage i_R.In addition, in another reverse gear shift R2, from second clutch K2, use gear stage i_4, i_5 and i_R, wherein in order to be coupled two minutes speed changers, open coupling S_ab1.In addition, in next reverse gear shift R3, from first clutch K1, use gear stage i_R, i_6 and i_4, wherein in order to be coupled two minutes speed changers, open coupling S_ab2.In creeper gear C1, from second clutch K2, use gear stage i_2, i_7 and i_3, wherein two minutes speed changers are coupled when coupling S_ab2 opens.In creeper gear C2, from second clutch K2, use gear stage i_2, i_7 and i_5, wherein two minutes speed changers are coupled when coupling S_ab2 opens.In the O1 of overgear, from second clutch K2, use gear stage i_4, i_3 and i_7, wherein two minutes speed changers are coupled by the switching member I being activated.In the O2 of overgear, from first clutch K1, use gear stage i_7, i_2 and i_4, wherein two minutes speed changers are coupled when coupling S_ab2 opens.
By the gearshift figure according to Fig. 4, drawn particularly, in the first forward gear G1, from first clutch K1, use gear stage i_3, i_4 and i_2, wherein two minutes speed changers are coupled mutually by the switching member K being activated.In the second forward gear G2, use gear stage i_2, in the 3rd forward gear G3, use gear stage i_3, in the 4th forward gear G4, use gear stage i_4, in the 5th forward gear G5, use gear stage i_5, in the 6th forward gear G6, use gear stage i_6, and use gear stage i_7 in the 7th forward gear G7.In the 8th forward gear G8, from first clutch K1, use gear stage i_3, i_4 and ZW_8, wherein in order to be coupled two minutes speed changers, activate switching member K.In addition, in reverse gear shift R1, from first clutch K1, use gear stage i_R.In addition, in another reverse gear shift R2, from second clutch K2, use gear stage i_6, i_7 and i_R, wherein two minutes speed changers are coupled when coupling S_ab1 opens.Finally in the O1 of overgear, from second clutch K2, use gear stage i_4, i_3 and i_7, wherein two minutes speed changers are coupled by the switching member K being activated.
By the gearshift figure according to Fig. 6, drawn particularly, at the first forward gear G1, from first clutch K1, using gear stage i_3, i_4 and i_2, wherein two minutes speed changers are coupled mutually by the switching member I being activated.In the second forward gear G2, use gear stage i_2, in the 3rd forward gear G3, use gear stage i_3, in the 4th forward gear G4, use gear stage i_4, in the 5th forward gear G5, use gear stage i_5, in the 6th forward gear G6, use gear stage i_6, and use gear stage i_7 in the 7th forward gear G7.In the 8th forward gear G8, from first clutch K1, use gear stage i_5, i_2 and i_4, wherein two minutes speed changers are coupled mutually by the switching member K being activated.In this external reverse gear shift R1, from second clutch K2, use gear stage x_5, i_5 and i_3, wherein two minutes speed changers are mutually coupled when coupling S_ab2 opens.In reverse gear shift R2, from first clutch K1, use gear stage i_3, i_6 and x_5, wherein in reverse gear shift R2, two minutes speed changers are mutually coupled when coupling S_ab1 opens.In reverse gear shift R3, from gear stage i_2, i_5 and i_R for second clutch K2, wherein two minutes speed changers are coupled mutually by the switching member K being activated.In addition, in reverse gear shift R4, from second clutch K2, use gear stage i_4, i_7 and i_R, wherein two minutes speed changers are mutually coupled when coupling S_ab1 opens.Finally in reverse gear shift R5, from second clutch K2, use gear stage i_2, i_R and i_3, when wherein within two minutes, speed changer coupling S_ab2 opens, be mutually coupled.In addition, in creeper gear C1, from second clutch K2, use gear stage i_2, i_5 and i_3, wherein two minutes speed changers are coupled mutually by switching member K.In creeper gear C2, from first clutch K1, use gear stage i_3, i_6 and i_2, wherein two minutes speed changers are coupled when coupling S_ab1 opens.In addition, in the O1 of overgear, from second clutch K2, use gear stage i_4, i_3 and i_7, wherein two minutes speed changers are coupled mutually by the switching member I being activated.In the O2 of overgear, from second clutch K2, use gear stage i_6, i_3 and i_5, wherein two minutes speed changers are coupled when coupling S_ab1 opens.Finally, in the O3 of overgear, from first clutch K1, use gear stage i_5, i_2 and i_6, wherein two minutes speed changers are coupled by the switching member K being activated.
By the gearshift figure by Fig. 8, drawn particularly, in the first forward gear G1, from first clutch K1, use gear stage i_3, i_4 and i_2, wherein two minutes speed changers are coupled by the switching member I being activated.In the second forward gear G2, use gear stage i_2, in the 3rd forward gear G3, use gear stage i_3, in the 4th forward gear G4, use gear stage i_4, in the 5th forward gear G5, use gear stage i_5, in the 6th forward gear G6, use gear stage i_6, and use gear stage i_7 in the 7th forward gear G7.In the 8th forward gear G8, from second clutch K2, use gear stage i_6, ZW_8 and i_3, wherein two minutes speed changers are coupled by the switching member K being activated.In addition, in reverse gear shift R1, from second clutch K2, use gear stage i_R, i_7 and ZW_8, wherein two minutes speed changers are coupled when coupling S_ab1 opens.In another reverse gear shift R2, from first clutch K1, use gear stage ZW_8, i_6 and i_R, wherein two minutes speed changers are coupled by switching member K.In another reverse gear shift R3, from first clutch K1, use gear stage i_3, i_R and i_2, wherein two minutes speed changers are mutually coupled when coupling S_ab1 opens.In creeper gear C1, from second clutch K2, use gear stage i_2, i_5 and i_3, wherein two minutes speed changers are mutually coupled when coupling S_ab2 opens.In addition, for overgear O1, from second clutch K2, use gear stage i_4, i_3 and i_7, wherein two minutes speed changers are coupled mutually by the switching member I activating.In the O2 of overgear, from second clutch K2, use gear stage i_6, i_5 and i_7, wherein two minutes speed changers are coupled when coupling S_ab2 opens.Finally, in the O3 of overgear, from first clutch K1, use gear stage i_7, i_4 and i_6, wherein two minutes speed changers are coupled when coupling S_ab1 opens.
By the gearshift figure according to Figure 10, drawn particularly, in the first forward gear G1, from first clutch K1, use gear stage i_3, i_4 and i_2, wherein two minutes speed changers are coupled by the switching member K being activated.In the second forward gear G2, use gear stage i_2, in the 3rd forward gear G3, use gear stage i_3, in the 4th forward gear G4, use gear stage i_4, in the 5th forward gear G5, use gear stage i_5, in the 6th forward gear G6, use gear stage i_6, and use gear stage i_7 in the 7th forward gear G7.In the 8th forward gear G8, use gear stage i_5, i_2 and i_4, wherein two minutes speed changers are coupled mutually by the switching member I being activated.In addition, in reverse gear shift R1, from first clutch K1, use gear stage i_3, x_5 and i_6, wherein two minutes speed changers are coupled when coupling S_ab2 opens.In another reverse gear shift R2, from first clutch K1, use gear stage i_3, x_5 and i_2, wherein two minutes speed changers are coupled when coupling S_ab2 opens.In next reverse gear shift R3, from second clutch K2, use gear stage i_4, i_R and i_5, wherein two minutes speed changers are mutually coupled when coupling S_ab2 opens.In reverse gear shift R4, from second clutch K2, use gear stage i_4, i_R and i_7, wherein two minutes speed changers are mutually coupled when coupling S_ab2 opens.Finally in reverse gear shift R5, from first clutch K1, use gear stage i_R.
In creeper gear C1, from second clutch K2, use gear stage i_2, i_5 and i_3, wherein two minutes speed changers are coupled mutually by switching member I.In addition, in next creeper gear C2, from second clutch K2, use gear stage i_2, i_7 and i_3, wherein two minutes speed changers are coupled when coupling S_ab1 opens.In the O1 of overgear, from second clutch K2, use gear stage i_4, i_3 and i_7, wherein two minutes speed changers are coupled mutually by switching member K.In addition, in the O2 of overgear, from first clutch K1, use gear stage i_5, i_2 and i_6, wherein two minutes speed changers are coupled mutually by switching member I.Finally, in the O3 of overgear, from first clutch K1, use gear stage i_7, i_2 and i_4, wherein two minutes speed changers are coupled when coupling S_ab1 opens.
In a word according to the first embodiment of Fig. 1 to 2, because gear stage i_2 and i_4 are arranged in an individual gears plane, utilizing two Double-gear planes and four individual gears planes and roundabout gear-switching member I to obtain the good speed ratio interval of low gear can matching.
Draw particularly in the first embodiment, in as Double-gear plane on the first gear plane 8-12, by free gear 8 for a forward gear G8, and by free gear 12 for a forward gear G6 and a reverse gear shift R3.In the second gear plane 9-2 as individual gears plane, by free gear 9 for five forward G1, G4, G8, O1, O2 and two reverse gear shift R2, R3.In the 3rd gear plane 3-13 as individual gears plane, by free gear 13 for five forward G1, G2, C1, C2, O2.In the 4th gear plane 10-14 as Double-gear plane, by free gear 10 for five forward G1, G3, G8, C1, O1, and by free gear 14 for three reverse gear shift R1, R2, R3.In the 5th gear plane 11-5 as individual gears plane, by free gear 11 for two forward gear G5, C2 and a reverse gear shift R2.Last in the 6th gear plane 6-15 as individual gears plane, by free gear 15 for five forward G7, C1, C2, O1, O2.
In a word, in according to the second embodiment of Fig. 3 and 4, utilize four Double-gear planes and roundabout gear-switching member K to obtain favourable axle and design bearing, because bear less load with the first jack shaft w_v1 of gear stage i_5, i_6, i_7 and the additional gear stage ZW_8 that uses in other forward gear.
In the second embodiment, draw particularly, in the first gear plane 8-12 as Double-gear plane, by free gear 8 for a forward gear G6 and a reverse gear shift R2, and by free gear 12 for two forward gear G1, G2.In the second gear plane 9-13 as Double-gear plane, by free gear 9 for a forward gear G8, and by free gear 13 for four forward gear G1, G4, G8, O1.In the 3rd gear plane 10-14 as Double-gear plane, by free gear 10 for two forward gear G7, O1 and a reverse gear shift R2, and by free gear 14 for four forward gear G1, G3, G8, O1.In the 4th gear plane 11-15 as Double-gear plane, by free gear 11 for a forward gear G5, and by free gear 15 for two reverse gear shift R1, R2.
In a word, according to the 3rd embodiment of Fig. 5 and 6, utilize two roundabout gear-switching member I and K and two Double-gear planes and three individual gears planes to obtain a good speed ratio interval with few structure consumes.In addition an other overgear O3 causes fuel saving.
In the 3rd embodiment, draw particularly, in the first gear plane 8-1 as individual gears plane, by free gear 8 for four forward gear G6, C2, O2, O3 and a reverse gear shift R2.In the second gear plane 9-13 as Double-gear plane, by free gear 9 for four forward gear G1, G4, G8, O1 and a reverse gear shift R4, and by free gear 13 for six forward gear G1, G2, G8, C1, C2, O3 and two reverse gear shift R3, R5.In the 3rd gear plane 10-3 as individual gears plane, by free gear 10 for six forward gear G1, G3, C1, C2, O1, O2 and three reverse gear shift R1, R2, R5.In the 4th gear plane 4-14 as individual gears plane, by free gear 14 for five forward G5, G8, C1, O2, O3 and two reverse gear shift R1, R3.In the 5th gear plane 11-15 as Double-gear plane, by free gear 11 for two forward gear G7, O1 and a reverse gear shift R4, and by free gear 15 for three forward gear R3, R4, R5.
In a word, according to the 4th embodiment of Fig. 7 and 8, utilize three Double-gear planes and two the individual gears planes preferably can matching by what use that the additional gear stage ZW_8 only using obtains speed ratio interval in a forward gear.
In the 4th embodiment, draw particularly, in the first gear plane 8-12 as Double-gear plane, by free gear 8 for three reverse gear shift R1, R2, R3, and by free gear 12 for three forward gear G1, G2, C2 and a reverse gear shift R3.In the second gear plane 9-2 as individual gears plane, by free gear 9 for four forward gear G1, G4, O1, O3.In the 3rd gear plane 3-13 as individual gears plane, by free gear 13 for four forward gear G6, G8, O2, O3 and a reverse gear shift R2.In the 4th gear plane 10-14 as Double-gear plane, by free gear 10 for five forward G1, G3, G8, C1, O1 and a reverse gear shift R3, and by free gear 14 for a forward gear G8 and two reverse gear shift R1, R2.In the 5th gear plane 11-15 as Double-gear plane, by free gear 11 for four forward gear G7, O1, O2, O3 and a reverse gear shift R1, and by free gear 15 for three forward gear G5, C1, O2.
In a word, according to the 5th embodiment of Fig. 9 and 10, utilize a Double-gear plane and five individual gears planes to obtain the speed ratio interval that can mate particularly well, because only have two gear levels (i_2 and i_4) to be relative to each other.
In the 5th embodiment, draw particularly, in the first gear plane 8-1 as individual gears plane, by free gear 8 for two forward gear G6, O2 and a reverse gear shift R1.In the second gear plane 9-13 as Double-gear plane, by free gear 9 for seven forward gear G1, G2, G8, C1, C2, O2, O3 and a reverse gear shift R2, and by free gear 13 for five forward G1, G4, G8, O1, O3 and two reverse gear shift R3, R4.In the 3rd gear plane 10-3 as individual gears plane, by free gear 10 for four forward gear G5, G8, C1, O2 and a reverse gear shift R3.In the 4th gear plane 4-14 as individual gears plane, by free gear 14 for five forward G1, G3, C1, C2, O1 and two reverse gear shift R1, R2.In the 5th gear plane 11-5 as individual gears plane, by free gear 11 for four forward gear G7, C2, O1, O3 and a reverse gear shift R4.Last in the 6th gear plane 6-15 as individual gears plane, by free gear 15 for three reverse gear shift R3, R4, R5.
Also can one or also can be in a plurality of embodiments for example, by least one additional gear stage ZW_x (ZW_8) for roundabout gear, this gear stage not be used in direct forward gear.The use of additional gear stage draws in the respective drawings of embodiment.
Also can by gear x1, x2 ... x7, x8 are for additional roundabout gear, and these gears can addedly add in individual gears plane, its middle gear x1, x2 ... the serial number of x7, x8 carries out as follows.Described serial number starts to be performed until the 4th gear x4 from the output stage i_ab_1 setting among the first gear x1 of the first jack shaft w_v1, the output stage i_ab_2 from setting wherein, with x5, represent the first gear on the second jack shaft w_v2, and other gear of continuous representation is until x8.If in the scope of reverse gear shift velocity ratio, use additional gear x1, x2 ... x7, x8, must for example by the intermediate gear ZR with on countershaft w_zw or like, carry out rotating speed reversion.
In all embodiments of dual-clutch transmission, repeatedly utilization due to the setting of some free gears, for keeping identical gear number need less gear plane and need thus less member, realized thus favourable structure space and saved and cost savings.
Irrelevant with corresponding embodiment, by numeral " 1 " in the grid of the corresponding form of Fig. 2,4,6,8 and 10 gearshift figure, mean, clutch K1, the K2 setting or coupling A, B, C, D, E, F, G, the H setting or the switching member I, the K that set are closed or be activated respectively.And mean at the blank grid by the corresponding form of Fig. 2,4,6,8 and 10 gearshift figure, clutch K1, the K2 setting or coupling A, B, C, D, E, F, G, the H setting or the switching member I, the K that set open respectively.
Different from above-mentioned rule, for be equipped on the coupling S_ab1 of output gear 17 or 18 or S_ab2 applicable be, for the blank grid according in the corresponding form of Fig. 2,4,6,8 and 10 gearshift figure, coupling S_ab1 or S_ab2 must open, and for have the grid of numeral " 1 " in by the corresponding form of Fig. 2,4,6,8 and 10 gearshift figure, coupling S_ab1 or S_ab2 should be closed.Must closed coupling S_ab1 in the grid with numeral " 1 " or S_ab2 in one group of gear, on the contrary in another group gear in the grid with numeral " 1 " coupling S_ab1 or S_ab2 both can open also can be closed.
In addition there is under many circumstances such possibility, insert being coupled or switching member of other, and do not affect kinetic current.Can realize gear preliminary election thus.
reference numerals list
The fixed gear of 1 second transmission input shaft
The fixed gear of 2 second transmission input shafts
The fixed gear of 3 second transmission input shafts
The fixed gear of 4 first transmission input shafts
The fixed gear of 5 first transmission input shafts
The fixed gear of 6 first transmission input shafts
The free gear of 7 first jack shafts
The free gear of 8 first jack shafts
The free gear of 9 first jack shafts
The free gear of 10 first jack shafts
The free gear of 11 first jack shafts
The free gear of 12 first jack shafts
The free gear of 13 second jack shafts
The free gear of 14 second jack shafts
The free gear of 15 second jack shafts
The fixed gear of 16 driven shafts
The output gear of 17 first jack shafts
The output gear of 18 second jack shafts
19 torshional vibration dampers
K1 first clutch
K2 second clutch
W_an live axle
W_ab driven shaft
W_v1 the first jack shaft
W_v2 the second jack shaft
W_k1 the first transmission input shaft
W_k2 the second transmission input shaft
A coupling
B coupling
C coupling
D coupling
E coupling
F coupling
G coupling
H coupling
The gear stage of i_2 the second forward gear
The gear stage of i_3 the 3rd forward gear
The gear stage of i_4 the 4th forward gear
The gear stage of i_5 the 5th forward gear
The gear stage of i_6 the 6th forward gear
The gear stage of i_7 the 7th forward gear
ZW_8 is for the additional gear stage of roundabout gear
X5 is for the gear of additional roundabout gear
Output stage on i_ab_1 the first jack shaft
Output stage on i_ab_2 the second jack shaft
G1 the first forward gear
G2 the second forward gear
G3 the 3rd forward gear
G4 the 4th forward gear
G5 the 5th forward gear
G6 the 6th forward gear
G7 the 7th forward gear
G8 the 8th forward gear
C1 creeper gear
C2 creeper gear
O1 overgear
O2 overgear
O3 overgear
R1 reverse gear shift
R2 reverse gear shift
R3 reverse gear shift
R4 reverse gear shift
R5 reverse gear shift
W_zw countershaft
ZR is for the intermediate gear of rotating speed reversion
The gear stage that ZS is used
I switching member
K switching member
Coupling in S_ab1 output stage, optional
Coupling in S_ab2 output stage, optional
N.lsb can not power gear shifting

Claims (19)

1. dual-clutch transmission, have: two clutches (K1, K2), the input side of described clutch is connected with a live axle (w_an) and the outlet side of described clutch is connected with in the transmission input shaft (w_k1, w_k2) of two mutual coaxial settings one respectively, at least two jack shafts (w_v1, w_v2), the rotatably mounted shift gear that is configured to free gear (8,9,10,11,12,13,14,15) on described two jack shafts, rotationally fixedly is arranged on shift gear on two transmission input shafts (w_k1, w_k2) and that be configured to fixed gear (1,2,3,4,5,6), and described fixed gear is meshed with free gear (8,9,10,11,12,13,14,15) at least in part, a plurality of couplings (A, B, C, D, E, F, G, H), for making free gear (8,9,10,11,12,13,14,15) rotationally fixedly be connected with jack shaft (w_v1, w_v2), be arranged on each output gear (17,18) on two jack shafts (w_v1, w_v2), described output gear is coupled mutually with the tooth portion of a driven shaft (w_ab) respectively, and at least one switching member (I, K), for two shift gear rotationally fixedlies are connected, wherein at least can connect a plurality of forward gear (1,2,3,4,5,6,7) and at least one reverse gear shift (R1 that can power gear shifting, R2, R3, R4, R5), it is characterized in that, be provided with maximum six gear plane (8-1, 8-12, 9-2, 9-13, 3-13, 10-3, 4-14, 10-14, 11-5, 11-15, 6-15), be wherein provided with at least one Double-gear plane (8-12, 9-13, 10-14, 11-15), and at each Double-gear plane (8-12, 9-13, 10-14, the first and second jack shaft (w_v1 11-15), w_v2) each free gear (8, 9, 10, 11, 12, 13, 14, 15) be equipped on transmission input shaft (w_k1, one of w_k2) a fixed gear (1, 2, 3, 4), wherein at each Double-gear plane (8-12, 9-13, 10-14, at least one free gear (8 11-15), 9, 10, 11, 12, 13, 14, 15) can be used at least two gears, thereby by least one switching member (I, K) can connect the roundabout gear that at least one can power gear shifting, by the first switching member (I) on the first jack shaft (w_v1), can make the free gear (9) of second minute speed changer and the free gear (10) of first minute speed changer be connected, thereby can connect as roundabout gear by this first switching member (I) first forward gear (G1) and/or the 8th forward gear (G8).
2. dual-clutch transmission as claimed in claim 1, it is characterized in that, be provided with a Double-gear plane (9-13) and five individual gears planes (8-1,10-3,4-14,11-5,6-15), wherein, in each individual gears plane (8-1,10-3,4-14,11-5,6-15), a free gear (8,10,11,14,15) of jack shaft (w_v1, w_v2) is equipped on a fixed gear (1,3,4,5,6) of one of transmission input shaft (w_k1, w_k2).
3. dual-clutch transmission as claimed in claim 1, is characterized in that, is provided with two Double-gear planes (8-12,10-14; 9-13,11-15) and at least three individual gears planes (8-1,10-3,4-14; 9-2,3-13,11-5,6-15), wherein at each individual gears plane (8-1,10-3,4-14; 9-2,3-13,11-5,6-15) in, a free gear (8,10,14 of jack shaft (w_v1, w_v2); 9,11,13,15) be equipped on a fixed gear (1,3,4 of one of transmission input shaft (w_k1, w_k2); 2,3,5,6).
4. dual-clutch transmission as claimed in claim 1, it is characterized in that, be provided with three Double-gear planes (8-12,10-14,11-15) and two individual gears planes (9-2,3-13), wherein, in each individual gears plane (9-2,3-13), a free gear (9,13) of jack shaft (w_v1, w_v2) is equipped on a fixed gear (2,3) of a transmission input shaft (w_k2).
5. dual-clutch transmission as claimed in claim 1, it is characterized in that, the first forward gear (G1) can be connected as roundabout gear respectively by the second switching member (K) being activated by the first switching member (I) and the 8th forward gear (G8) that are activated, or the first forward gear (G1) can be connected as roundabout gear respectively by the first switching member (I) being activated by the second switching member (K) and the 8th forward gear (G8).
6. dual-clutch transmission as claimed in claim 1, it is characterized in that, as three fixed gears (1,2,3) on the first gear plane (8-12) of Double-gear plane and the second transmission input shaft (w_k2) of comprising second minute speed changer as the second gear plane (9-2) and the 3rd gear plane (3-13) of individual gears plane respectively.
7. dual-clutch transmission as claimed in claim 6, it is characterized in that two fixed gears (4,5) on the first transmission input shaft (w_k1) that comprises first minute speed changer as the 4th gear plane (10-14) and the 5th gear plane (11-15) of Double-gear plane respectively.
8. dual-clutch transmission as claimed in claim 6, it is characterized in that, as three fixed gears (4,5,6) on the 4th gear plane (10-14) of Double-gear plane and the first transmission input shaft (w_k1) of comprising first minute speed changer as the 5th gear plane (11-5) and the 6th gear plane (6-15) of individual gears plane respectively.
9. dual-clutch transmission as claimed in claim 1, it is characterized in that, as the first gear plane (8-1) of individual gears plane with comprise two fixed gears (1,2) on second transmission input shaft (w_k2) of second minute speed changer as the second gear plane (9-13) of Double-gear plane.
10. dual-clutch transmission as claimed in claim 9, it is characterized in that, respectively as the 3rd gear plane (10-3) of individual gears plane and the 4th gear plane (4-14) and comprise three fixed gears (3,4,5) on first transmission input shaft (w_k1) of first minute speed changer as the 5th gear plane (11-15) of Double-gear plane.
11. dual-clutch transmissions as claimed in claim 9, it is characterized in that, as the 3rd gear plane (10-3), the 4th gear plane (4-14), the 5th gear plane (11-5) and the 6th gear plane (6-15) of individual gears plane, comprise four fixed gears (3,4,5,6) on first transmission input shaft (w_k1) of first minute speed changer respectively.
12. dual-clutch transmissions as claimed in claim 1, it is characterized in that, the first forward gear (G1) can be connected as roundabout gear by first clutch (K1) and the 6th coupling (F) being activated and the first switching member (I) being activated, the second forward gear (G2) can be connected by second clutch (K2) and the 6th coupling (F) being activated, the 3rd forward gear (G3) can be connected by first clutch (K1) and the 3rd coupling (C) being activated, the 4th forward gear (G4) can be connected by second clutch (K2) and the second coupling being activated (B), the 5th forward gear (G5) can be connected by first clutch (K1) and the 4th coupling (D) being activated, the 6th forward gear (G6) can be connected by second clutch (K2) and the 5th coupling (E) being activated, the 7th forward gear (G7) can be connected by first clutch (K1) and the 8th coupling (H) being activated, the 8th forward gear (G8) can be connected as roundabout gear by first clutch (K1) and the first coupling being activated (A) and the first switching member (I) being activated, first reverse gear shift (R1) can be connected by first clutch (K1) and the 7th coupling (G) being activated, and/or second reverse gear shift (R2) can pass through second clutch (K2), the second coupling (B) being activated, the 4th coupling (D) being activated and the 7th coupling (G) being activated and as roundabout gear, connect when the coupling (S_ab1) that is equipped on the output gear (17) of the first jack shaft is opened, and/or the 3rd reverse gear shift (R3) can pass through first clutch (K1), the second coupling (B) being activated, the 5th coupling (E) being activated and the 7th coupling (G) being activated and as roundabout gear, connect when the coupling (S_ab2) that is equipped on the output gear (18) of the second jack shaft is opened.
13. dual-clutch transmissions as claimed in claim 12, it is characterized in that, first creeper gear (C1) can pass through second clutch (K2), the 3rd coupling (C) being activated, the 6th coupling (F) being activated and the 8th coupling (H) being activated and as roundabout gear, connect when the coupling (S_ab2) that is equipped on the output gear (18) of the second jack shaft is opened, and/or second creeper gear (C2) can pass through second clutch (K2), the 4th coupling (D) being activated, the 6th coupling (F) being activated and the 8th coupling (H) being activated and as roundabout gear, connect when the coupling (S_ab2) that is equipped on the output gear (18) of the second jack shaft is opened, and/or second clutch (K2) can be passed through in an overgear (O1), the 8th coupling (H) being activated and the first switching member (I) being activated are connected as roundabout gear, and/or first clutch (K1) can be passed through in an overgear (O2), the second coupling (B) being activated, the 6th coupling (F) being activated and the 8th coupling (H) being activated and as roundabout gear, connect when the coupling (S_ab2) that is equipped on the output gear (18) of the second jack shaft is opened.
14. dual-clutch transmissions as claimed in claim 1, it is characterized in that, the first forward gear (G1) can be connected as roundabout gear by first clutch (K1) and the 6th coupling (F) being activated and the first switching member (I) being activated, the second forward gear (G2) can be connected by second clutch (K2) and the 6th coupling (F) being activated, the 3rd forward gear (G3) can be connected by first clutch (K1) and the 3rd coupling (C) being activated, the 4th forward gear (G4) can be connected by second clutch (K2) and the second coupling being activated (B), the 5th forward gear (G5) can be connected by first clutch (K1) and the 7th coupling (G) being activated, the 6th forward gear (G6) can be connected by second clutch (K2) and the first coupling being activated (A), the 7th forward gear (G7) can be connected by first clutch (K1) and the 4th coupling (D) being activated, the 8th forward gear (G8) can be connected as roundabout gear by first clutch (K1) and the second coupling being activated (B) and the second switching member (K) being activated, the first reverse gear shift (R1) can pass through second clutch (K2), the 3rd coupling (C) being activated, the 5th coupling (E) being activated and the 7th coupling (G) being activated and as roundabout gear, connect when the coupling (S_ab2) that is equipped on the output gear (18) of the second jack shaft is opened, and/or second reverse gear shift (R2) can pass through first clutch (K1), the first coupling (A) being activated, the 3rd coupling (C) being activated and the 5th coupling (E) being activated and as roundabout gear, connect when the coupling (S_ab1) that is equipped on the output gear (17) of the first jack shaft is opened, and/or the 3rd reverse gear shift (R3) can as roundabout gear, connect by second clutch (K2) and the 8th coupling (H) being activated and the second switching member (K) being activated, and/or the 4th reverse gear shift (R4) can pass through second clutch (K2), the second coupling (B) being activated, the 4th coupling (D) being activated and the 8th coupling (H) being activated and as roundabout gear, connect when the coupling (S_ab1) that is equipped on the output gear (17) of the first jack shaft is opened, and/or the 5th reverse gear shift (R5) can pass through second clutch (K2), the 3rd coupling (C) being activated, the 6th coupling (F) being activated and the 8th coupling (H) being activated and as roundabout gear, connect when the coupling (S_ab2) that is equipped on the output gear (18) of the second jack shaft is opened.
15. dual-clutch transmissions as claimed in claim 14, it is characterized in that, first creeper gear (C1) can be connected as roundabout gear by second clutch (K2) and the 3rd coupling (C) being activated and the second switching member (K) being activated, and/or second creeper gear (C2) can pass through first clutch (K1), the first coupling (A) being activated, the 3rd coupling (C) being activated and the 6th coupling (F) being activated and as roundabout gear, connect when the coupling (S_ab1) that is equipped on the output gear (17) of the first jack shaft is opened, and/or an overgear (O1) can be connected as roundabout gear by second clutch (K2) and the 4th coupling (D) being activated and the first switching member (I) being activated, and/or second clutch (K2) can be passed through in an overgear (O2), the first coupling (A) being activated, the 3rd coupling (C) being activated and the 7th coupling (G) being activated and as roundabout gear, connect when the coupling (S_ab1) that is equipped on the output gear (17) of the first jack shaft is opened, and/or an overgear (O3) can be connected as roundabout gear by first clutch (K1) and the first coupling being activated (A) and the second switching member (K) being activated.
16. dual-clutch transmissions as claimed in claim 1, it is characterized in that, the first forward gear (G1) can be connected as roundabout gear by first clutch (K1) and the 5th coupling (E) being activated and the first switching member (I) being activated, the second forward gear (G2) can be connected by second clutch (K2) and the 5th coupling (E) being activated, the 3rd forward gear (G3) can be connected by first clutch (K1) and the 3rd coupling (C) being activated, the 4th forward gear (G4) can be connected by second clutch (K2) and the second coupling being activated (B), the 5th forward gear (G5) can be connected by first clutch (K1) and the 8th coupling (H) being activated, the 6th forward gear (G6) can be connected by second clutch (K2) and the 6th coupling (F) being activated, the 7th forward gear (G7) can be connected by first clutch (K1) and the 4th coupling (D) being activated, the 8th forward gear (G8) can be connected by second clutch (K2) and the 3rd coupling (C) being activated and the second switching member (K) being activated, the first reverse gear shift (R1) is by second clutch (K2), the first coupling (A) being activated, the 4th coupling (D) being activated and the 7th coupling (G) being activated and as roundabout gear, connect when the coupling (S_ab1) that is equipped on the output gear (17) of the first jack shaft is opened, and/or second reverse gear shift (R2) can as roundabout gear, connect by first clutch (K1) and the first coupling being activated (A) and the second switching member (K) being activated, and/or the 3rd reverse gear shift (R3) can pass through first clutch (K1), the first coupling (A) being activated, the 3rd coupling (C) being activated and the 5th coupling (E) being activated and as roundabout gear, connect when the coupling (S_ab1) that is equipped on the output gear (17) of the first jack shaft is opened.
17. dual-clutch transmissions as claimed in claim 16, it is characterized in that, first creeper gear (C1) can pass through second clutch (K2), the 3rd coupling (C) being activated, the 5th coupling (E) being activated and the 8th coupling (H) being activated and as roundabout gear, connect when the coupling (S_ab2) that is equipped on the output gear (18) of the second jack shaft is opened, and/or second clutch (K2) can be passed through in an overgear (O1), the 4th coupling (D) being activated and the first switching member (I) being activated are connected as roundabout gear, and/or second clutch (K2) can be passed through in an overgear (O2), the 4th coupling (D) being activated, the 6th coupling (F) being activated and the 8th coupling (H) being activated and as roundabout gear, connect when the coupling (S_ab2) that is equipped on the output gear (18) of the second jack shaft is opened, and/or an overgear (O3) is by first clutch (K1), the second coupling (B) being activated, the 4th coupling (D) being activated and the 6th coupling (F) being activated and as roundabout gear, connect when the coupling (S_ab1) that is equipped on the output gear (17) of the first jack shaft is opened.
18. dual-clutch transmissions as claimed in claim 1, it is characterized in that, the first forward gear (G1) can be connected as roundabout gear by first clutch (K1) and the second coupling being activated (B) and the second switching member (K) being activated, the second forward gear (G2) can be connected by second clutch (K2) and the second coupling being activated (B), the 3rd forward gear (G3) can be connected by first clutch (K1) and the 7th coupling (G) being activated, the 4th forward gear (G4) can be connected by second clutch (K2) and the 6th coupling (F) being activated, the 5th forward gear (G5) can be connected by first clutch (K1) and the 3rd coupling (C) being activated, the 6th forward gear (G6) can be connected by second clutch (K2) and the first coupling being activated (A), the 7th forward gear (G7) can be connected by first clutch (K1) and the 4th coupling (D) being activated, the 8th forward gear (G8) can be connected as roundabout gear by first clutch (K1) and the 6th coupling (F) being activated and the first switching member (I) being activated, the first reverse gear shift (R1) can be by first clutch (K1) and the first coupling being activated (A), the 5th coupling (E) being activated and the 7th coupling (G) being activated and as roundabout gear, connect when the coupling (S_ab2) that is equipped on the output gear (18) of the second jack shaft is opened, and/or second reverse gear shift (R2) can pass through first clutch (K1), the second coupling (B) being activated, the 5th coupling (E) being activated and the 7th coupling (G) being activated and as roundabout gear, connect when the coupling (S_ab2) that is equipped on the output gear (18) of the second jack shaft is opened, and/or the 3rd reverse gear shift (R3) can pass through second clutch (K2), the 3rd coupling (C) being activated, the 6th coupling (F) being activated and the 8th coupling (H) being activated and as roundabout gear, connect when the coupling (S_ab2) that is equipped on the output gear (18) of the second jack shaft is opened, and/or the 4th reverse gear shift (R4) can pass through second clutch (K2), the 4th coupling (D) being activated, the 6th coupling (F) being activated and the 8th coupling (H) being activated and as roundabout gear, connect when the coupling (S_ab2) that is equipped on the output gear (18) of the second jack shaft is opened, and/or the 5th reverse gear shift (R5) can connect by first clutch (K1) and the 8th coupling (H) being activated.
19. dual-clutch transmissions as claimed in claim 18, it is characterized in that, first creeper gear (C1) can be connected as roundabout gear by second clutch (K2) and the 7th coupling (G) being activated and the first switching member (I) being activated, and/or second creeper gear (C2) can pass through second clutch (K2), the second coupling (B) being activated, the 4th coupling (D) being activated and the 7th coupling (G) being activated and as roundabout gear, connect when the coupling (S_ab1) that is equipped on the output gear (17) of the first jack shaft is opened, and/or an overgear (O1) can be connected as roundabout gear by second clutch (K2) and the 4th coupling (D) being activated and the on-off system (K) being activated, and/or an overgear (O2) can be connected as roundabout gear by first clutch (K1) and the first coupling being activated (A) and the first switching member (I) being activated, and/or first clutch (K1) can be passed through in an overgear (O3), the second coupling (B) being activated, the 4th coupling (D) being activated and the 6th coupling (F) being activated and open as roundabout gear and connect at the coupling (S_ab1) that is equipped on the output gear (17) of the first jack shaft.
CN201010163898.6A 2009-04-14 2010-04-13 Double clutch transmission Expired - Fee Related CN101865250B (en)

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Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8424404B2 (en) * 2011-01-10 2013-04-23 GM Global Technology Operations LLC Eight speed dual clutch transmissions
DE102011088605B4 (en) * 2011-12-14 2021-02-18 Zf Friedrichshafen Ag Double clutch
DE102013216385A1 (en) 2013-08-19 2015-02-19 Volkswagen Aktiengesellschaft Double clutch transmission for a motor vehicle
DE102013216384A1 (en) 2013-08-19 2015-02-19 Volkswagen Aktiengesellschaft Double clutch
DE102015213923A1 (en) 2015-07-23 2017-01-26 Volkswagen Aktiengesellschaft Double clutch
DE102015220659B4 (en) * 2015-10-22 2020-11-26 Zf Friedrichshafen Ag Dual clutch transmission for a vehicle
DE102016202915A1 (en) 2016-02-25 2017-08-31 Ford Global Technologies, Llc Dual-clutch transmission for motor vehicles
DE102016202914A1 (en) 2016-02-25 2017-08-31 Ford Global Technologies, Llc Dual-clutch transmission for motor vehicles
AT524034B1 (en) * 2020-11-04 2022-02-15 Avl List Gmbh DRIVE TRAIN FOR A MOTOR VEHICLE

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10239540A1 (en) * 2001-07-15 2004-03-11 Boisch, Richard, Prof. Dr. Reverse gear with central synchromesh for load switch transmissions has first-gear countershafts with direct gear connection
DE102004001961A1 (en) * 2004-01-13 2005-08-04 Boisch, Richard, Prof. Dr. Powershift transmission with additional gears
CN1910387A (en) * 2004-01-07 2007-02-07 大众汽车有限公司 Twin clutch transmission for a motor vehicle
CN101802446A (en) * 2007-10-15 2010-08-11 腓特烈斯港齿轮工厂股份公司 Dual clutch transmission

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3822330A1 (en) * 1988-01-09 1989-07-27 Rudolf Prof Dr Ing Franke Spur-wheel change-speed gearbox, particularly for motor vehicles
DE10305241A1 (en) * 2003-02-08 2004-09-23 Zf Friedrichshafen Ag Double clutching transmission for six-speed or seven-speed motor vehicle has two fixed gears arranged on first transmission input shaft, and at least one fixed gear arranged on second transmission shaft
US7246536B2 (en) * 2005-03-17 2007-07-24 Ford Global Technologies, Llc Dual clutch kinematic arrangements with wide span
DE102005028532B4 (en) * 2005-06-18 2007-06-21 Boisch, Richard, Prof. Dr. Modular (powershift) transmission
DE102007049264B4 (en) * 2007-10-15 2017-05-11 Zf Friedrichshafen Ag Double clutch
DE102007049269B4 (en) * 2007-10-15 2017-05-18 Zf Friedrichshafen Ag Double clutch
DE102007049260B4 (en) * 2007-10-15 2017-07-27 Zf Friedrichshafen Ag Double clutch
DE102007049257B4 (en) * 2007-10-15 2017-05-18 Zf Friedrichshafen Ag Double clutch

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10239540A1 (en) * 2001-07-15 2004-03-11 Boisch, Richard, Prof. Dr. Reverse gear with central synchromesh for load switch transmissions has first-gear countershafts with direct gear connection
CN1910387A (en) * 2004-01-07 2007-02-07 大众汽车有限公司 Twin clutch transmission for a motor vehicle
DE102004001961A1 (en) * 2004-01-13 2005-08-04 Boisch, Richard, Prof. Dr. Powershift transmission with additional gears
CN101802446A (en) * 2007-10-15 2010-08-11 腓特烈斯港齿轮工厂股份公司 Dual clutch transmission

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